Fluid transferring apparatus



Jan. 9 1968 N. E JAMESON FLUID TRANSFERRING APPARATUS 4 Sheets-Sheet 1 Filed March 2, 1964 INVENTOIi um. a. amzsou ATTORNEY N. E. JAMESON FLUID TRANSFERRING APPARATUS Jan. 9, 1968 4 Sheets-:Sheet 3 Filed March 2. 1964 2- INVENTOR J NEAL s. JAMESON ATTORNEY I Jan. 9, 1968 NLE. JAMESON FLUID TRANSFERRING APPARATUS 4 Sheets-Sheet 4 Filed March 1964 ATTORNEY United States Patent 3,362,432 FLUID TRANSFERG APPARATUS Neal E. Jameson, Grange, 'Calif., assignor to FMC Corporation, San Jose, Calif., a corporation of Delaware Filed Mar. 2, 1964, Ser. No. 348,606 6 Claims. (Cl. 137-615) The present invention pertains to a fluid transferring apparatus and more particularly to an articulated fluid transferring arm having a single counterweight which imposes dual counteracting turning moments on the arm.

In general, an articulated fluid transferring arm includes a rigid inner boom pivoted for elevational movement, an outer boom pivoted on the inner boom for elevational movement with respect thereto, a coupling pivoted on the outer boom and adapted for connection to an intake or discharge manifold of a tank on a ship, airplane, truck, or the like, and mechanism for controlling the elevational movement of the booms in order to move the coupling into and out of coupling position. Either the booms are tubular and interconnected for conducting fluid to and from the coupling or else a separate flexible hose is supported by the booms and attached to the coupling. It has been known to use powered devices, such as a hydraulic cylinder, as the control mechanism for adjusting the booms. It has also been known to use counterweights for this purpose. The present invention is primarily concerned with the type of fluid transferring arm that uses counterweights, and particularly only a single counterweight, for overcoming both the turning moment of the inner and outer booms about the pivot axis of the inner boom and the turning moment of the outer boom about its pivot axis on the inner boom.

It is an object of the present invention to provide improvements in an articulated fluid transferring arm.

Another object is to provide an articulated fluid transferring arm having a single counterweight which imposes dual counteracting turning moments on the arm so that the turning moments about both the inner and outer axes of the arm are counteracted.

Another object is to provide a fluid transferring arm of the type described in which the counterweight is suspended in a low position so as to avoid column bending, to eliminate problems of windage and earthquake in the design of the arm, and to maintain as low a center of gravity as is possible.

Another object is to provide a fluid transferring arm which has a maximum range of movement, which can project both of its booms vertically upward in axial alignment, and which can swing overhead throughout an angle of greater than 180 so as to be able to provide fluid transferring service on opposite sides thereof.

Another object is to provide a fluid transferring arm having counterweight control wherein the distance of the counterweight from the moment center is adjustable.

Another object is to provide a constantly balanced fluid transferring arm which is easy to move by hand, which reduces flange loadings, and which does not require an external source of power although it is capable of being so powered.

These, together with other objects, will become apparent upon reference to the following description and accompanying drawings, in which:

FIGURE 1 is a side elevation of a fluid transferring arm embodying the present invention and being mounted on a pier.

FIGURE 2 is an enlarged fragmentary plan of a portion of the arm.

FIGURE 3 is a side elevation taken from a position indicated by line 3--3 in FIG. 2.

FIGURE 4 is a rear elevation of the arm shown in FIG. 1.

3,362,432 Patented Jan. 9, 1968 FIGURE 5 is a diagrammatic view which is subsequently employed herein to aid in describing the turning moments which are set up with the subject arm.

FIGURE 6 is a side elevation of the subject arm showing, in full lines, the arm in a different position from FIG. 1 and, in phantom, other positions of the arm, this view particularly showing the ability of the arm to swing overhead throughout an angle of greater than 180".

FIGURE 7 is a fragmentary side elevation of a portion of another form of the subject fluid transferring arm.

FIGURE 8 is a plan of the portion of the arm shown in FIG. 7.

A fluid transferring arm 12 embodying the present invention is shown in FIGS. 1 and 4 as being mounted on a pier or platform 15. A main support bracket 16 is rigidly secured to the pier and supports a riser 18 having a lower portion adapted to be connected to a fluid container, not shown, and an upright portion 19. A riser swivel joint 20 is connected to the upright portion and provides a vertical axis of rotation 21. An elbow 22 is connected to the riser swivel joint and has a horizontal portion 24 projecting laterally (FIGS. 2 and 4) from the upright portion of the riser. An inner swivel joint 25, establishing a horizontal fulcrum axis 26, is connected to the horizontal portion of the elbow.

A rigid tubular inner boom 30 has an intermediate straight portion 31, an inner elbow 32 including a horizontal portion 33 connected to the inner swivel joint 25, and an outer elbow 34 including an outer horizontal portion 35. An outer swivel joint 37 is connected to this outer horizontal portion and establishes an outer axis 38 which is parallel to the fulcrum axis 26.

The fluid transferring arm 12 also includes a rigid tubular outer boom 45 having a straight intermediate portion 46, and an inner elbow 47 including a horizontal portion 48 connected to the outer swivel joint 37 so that the outer boom is pivotally connected in fluid communicating rela tion with the inner boom for elevational pivotal movement about the outer axis. The outer boom also has an outer elbow 49. An outer sheave 50 is rigidly connected to the horizontal portion 48 of the inner elbow 47 in coaxial relation with the outer axis 38. As best shown in FIG. 4, this outer sheave is located in a vertical plane between the inner and outer booms 30 and 45.

A coupling 55 is connected to the outer elbow 49 by a swivel joint 56 which provides a horizontal coupling axis 58. The coupling also includes swivel joints 59 and 6t) and a flange 61. Because of the joints 59 and 60, the flange is adjustable about axes 63 and 64.

A mounting plate 70 (FIGS. 2 and 3) includes a forward section 71 secured, as by welding, to the inner boom 30, an intermediate section 72 similarly secured to the horizontal portion 33 of the inner boom, and a rear section 73 projecting on the opposite side of the axis 26 from the inner boom. In effect, therefore, the inner boom and the plate together constitute boom means fulcrummed on the axis 26.

A shaft 76 is journaled in the rear section 73 and is parallel to the inner axis 26. The shaft has opposite ends 77 and 73 on opposite sides of the mounting plate 70. An inner sheave 80, whose axis is identified by number 81, is secured to one end 78 of the shaft for rotation with the shaft. The inner sheave is of the same diameter and is in a common vertical plane with the outer sheave 50 (FIGS. 1 and 4). A cable 82 is wrapped around the sheaves and is connected thereto so that rotation of one of the sheaves imparts rotation to the other sheave. Turnbuckles 84 are provided in the cable for adjusting the tension thereon.

A long radius link (FIGS. 2 and 3) is rigidly secured to the end 77 of the shaft 76, whereas a short radius link 91 (FIGS. 1 and 2) is secured to the inner sheave 80, on the outside surface thereof, and in parallel relation to the long radius link. Each link has a longitudinal slot 92 (FIG. 3) therein, and blocks 94 are adjustably slidably mounted in the slots. Axially fixed, rotatable, threaded bolts 96 extend longitudinally through the slots and are threaded through the blocks. Thus, rotation of the bolts causes longitudinal movement of the blocks in their respective slots.

Straight rigid bars 100 have upper ends pivoted individually to the blocks 94 and lower ends pivoted to a counterweight 102. The counterweight includes a receptacle 104 which receives, for example, ingots of various weight, in order to adjust the downward force of the counterweight. The receptacle includes side flanges 106 which are individually pivoted to the lower ends of the bars 100. In this manner, the counterweight is suspended from the inner sheave 80 in radially spaced relation to the axis thereof, and the points of suspension of the counterweight, represented by the blocks 94, are adjustable toward and away from the axis of the sheave 80.

It is also to be noted (FIG. 2) that the counterweight 102 has a side 108 which is laterally displaced from the upright portion 19 of the riser 18 so as to be able to pass thereby during overhead swinging of the arm 12 in a manner to be described. Furthermore, the counterweight has a bottom 110 which is spaced above the pier 15 when the inner and outer booms 30 and 45 extend vertically upward in alignment or, in other words, when the counterweight is at its lowest suspended position.

A very important advantage of the subject fluid transferring arm 12 is the ability of the single counterweight 102 to maintain the arm in balance irrespective of the positions of the booms 30 and 45. It is, of course, understood that reference to a single counterweight means the total weight of the counterweight 102 notwithstanding the several individual weights or ingots in the receptacle 104. The balance of the arm by the single counterwegiht is best explained by reference to FIG. which is a simplified diagram of the arm. It is to be noted that there are two turning moments to consider. First, there is a turning moment imposed by both the inner boom and the outer boom 45 about the axis 26. Secondly, there is a turning moment imposed by just the outer boom 45 about the axis 38. The counterweight 102 imposes a turning moment which counteracts the turning moment of the inner and outer booms about the axis 26 irrespective of the position of the inner and outer booms. As the inner boom pivots in a clockwise direction, and assuming the outer boom remains perpendicular to the inner boom, the combined center of gravity of the inner and outer booms first moves farther from the axis 26 than it is in FIG. 5; correspondingly, the points of suspension of the counterweight, represented by the blocks 94, move farther from the axis 26 by an amount which maintains a balance between the two turning moments about axis 26. If clockwise movement of the inner boom continues, said combined center of gravity and the blocks 94 eventually move closer to axis 26, a balance being maintained in all positions. The same balance is maintained if the boom 30 moves in a counterclockwise direction about the axis 26.

With the inner boom 30 (FIG. 3) in its horizontal position, however, if the outer boom 45 is swung forward to position 45a, the turning moment of the outer boom about the outer axis 38 increases. Because of the unitary rotation of the inner and outer sheaves 80 and 50, the blocks or points of suspension 94 move rearward so that the bars 100 are in positions 100a thereby increasing the turning moment imposed by the counterweight 102 about the axis 81 by an amount which exactly counteracts the turning moment of the outer boom about the axis 38. Further, if the outer boom is moved rearward to position 4511, the bars 100 are moved forward to positions 1001) thereby maintaining a balance of the turning moments about axis 38 Or 81.

It is important to note that movement of the outer boom 45 about the axis 38 does not disturb the balance of the inner boom 30; in other words, as the outer boom 45 moves between positions 45a and 45b, the inner boom remains in whatever position it previouslyw as in, such as horizontal in FIG. 5. The reason is that movement of boom 45 to position 45a, for example, increases the counterclockwise turning moment about axis 26, but since the bars move to position a, the counteracting or clockwise turning moment about axis 26 also increases; therefore, the inner boom does not move.

Although only a small angle of movement of the outer boom 45 has been illustrated in FIG. 5, the outer boom can move in nearly a three-hundred and sixty degree circle about the axis 38.

Another important advantage of the subject arm is its ability to swing overhead and throughout an angle of greater than one-hundred and eighty degrees. This is best illustrated by reference to FIG. 6. This type of movement is particularly desirable on so-called finger (that is, very narrow) piers from which it is desired to service ships on opposite sides of the pier. Certain prior art loading arms have been able to do this, but it has been necessary to rotate the arm about its vertical axis in order to move the coupling, as 55, from a position on one side of the pier to a position on the opposite side of the pier. Such movement about a vertical axis may not be possible with conventional arms if they are situated side-by-side in a bank. Expressed otherwise, it has been necessary to space adjacent prior art loading arms farther apart than desirable in order to accommodate such swinging movement about the vertical axis.

In FIG. 6 position A shows both the inner and outer booms 30 and 45 (although broken away) projecting horizontally outward in alignment from the axis 26. Although not shown, the inner boom could project downward until it engages the pier, andthe outer boom could project downward from the inner boom, if it were necessary to reach a low manifold flange on a ship, not shown. Position B in FIG. 6 shows the inner boom extending vertically upward and the outer boom projecting outward in perpendicular relation to the inner boom. The outer boom can be swung into a vertical position, not shown, where it is aligned with the inner boom, it being noted that the counterweight 102 would then be in its lowest point of suspension. Position C in FIG. 6 shows the inner boom vertical and the outer boom projecting perpendicularly to the inner boom on the opposite side from position B. Position D in FIG. 6 shows the inner and outer booms projecting horizontally from the inner axis in the opposite direction from position A. It is believed understood that the arm could extend even farther down than position D into a position similar to that discussed above in regard to position A. In swinging from one side of the axis 26 to the other, it will be noted that the coupling 55 must be rotated about its axis 63 in order to bring the flange 61 into a position for attachment to a manifold flange 115. During all of the described movements of the inner and outer booms, counterbalance is maintained about the inner and outer axes, according to the same principles explained in connection with FIG. 5. Because the inner and outer sheaves must be able to rotate through nearly three-hundred and sixty degrees, the cable 82 is wrapped around the sheaves before it is connected thereto.

The coupling 55 can also be rotated about axis 58 in order to attach flange 61 to a horizontal manifold flange, as 115' in FIG. 6, position B.

A second form of the subject arm is illustrated in FIGS. 7 and 8. In several respects, the arm of FIGS. 8 and 7 is the same as the arm illustrated in FIGS. 1 through 6 and corresponding parts are given the same number although followed by a prime. Thus, a riser 18 supports an inner boom 30' for elevational pivotal move ment about an inner axis 26. A mounting plate 70' includes a forward section 71' secured to the inner boom and a pair of rear sections 120 projecting from the opposite side of the axis 26' from the inner boom 30 and in spaced parallel relation to each other. A shaft 121 rigidly interconnects the rear sections, and a rear sheave 123 is rotatably journaled on this shaft in a common vertical plane with the outer sheave, not shown, but exactly like the outer sheave 50. A cable 82' is wrapped around and connected to these inner and outer sheaves.

Rigid L-shaped bars 130 have upper ends 131 pivoted by pins 132 to opposite sides of the inner sheave 123 in radially spaced relation to its axis of rotation defined by the shaft 121. These L-shaped bars also have lower ends 135 pivotally connected to a counterweight 102' by pins 138. Although not shown, the pins 132 could be mounted on a block, as 94, for adjustment toward and away from the shaft 121.

In operation, the form of the apparatus shown in FIGS. 7 and 8 maintains a counterbalance according to the same principles explained in reference to FIG. 5.

Although it can move into a position with both of its booms, as 30', projecting vertically upward and can project to a certain extent on opposite sides of the axis 26', the form of the arm illustrated in FIGS. 7 and 8 does not have as full a range of movement as the arm of FIGS. 1 through 6.

From the foregoing, it will be understood that the subject fluid transferring arm 12 uses only a single counterweight for imposing dual counteracting turning moments on the arm with the result that the inner and outer booms, together, are balanced about the inner axis of the arm, and the outer boom, alone, is balanced about the outer axis of the arm, these balances being, in effect, independent of each other so that either boom remains in whatever position it is placed. Thus, the arm is easy to move by hand, reduce loads on flanges to which it is connected, and does not require, although may use, an external source of power. Furthermore, because of the overhead swinging ability of the arm, it can be employed for servicing tanks on diametrically opposite sides of the arm. This full range of movement makes the arm readily adapted for transferring fluid to and from ships, airplanes, tank trucks, and the like. Furthermore, by suspending the counterweight from the arm, in all positions of the booms, the center of gravity of the entire arm is maintained at a low level. Since the counterweight does not project upward, windage and earthquake forces are less and can even be disregarded in the design of the arm. Still further, there is no problem or columnar bending with the counterweight suspended in this manner. In addition, the point of suspension of the counterweight is adjustable toward and away from the moment axes so that the counteracting turning moments can be varied as required.

Although preferred embodiments of the present invention have been shown and described, it will be understood that various changes and modifications may be made in the details thereof without departing from the spirit and scope of the appended claims.

Having described the invention, what is claimed as new and desired to be secured by Letters Patent is as follows: i

1. In a fluid transferring apparatus, a tubular fluidconducting inner boom pivoted for elevational movement about a fulcrum, a tubular fluid-conducting outer boom pivoted in fluid-tight relation to the inner boom for elevational movement through substantially 360 with respect thereto about an outer axis, an outer sheave secured to the outer boom in coaxial relation with the outer axis, an inner sheave, means mounting the inner sheave on the inner boom so that the axis of rotation of the inner sheave is on the opposite side of the fulcrum from said outer axis, a cable interconnecting the inner and outer sheaves for unitary rotation about their respective axes, a counterweight, and means pivotally mounting the counterweight on the inner sheave so that the counterweight is positioned below the inner sheave irrespective of the positions of the booms and so that the counterweight imposes a first turning moment about said fulcrum which counteracts the turning moment of the inner and outer booms about the fulcrum and a second turning moment about said inner sheaves axis which counteracts the turning moment of the outer boom about said outer axis.

2. The apparatus of claim 1 including a support, and means mounting the inner boom on the support for pivotal movement about said fulcrum between positions projecting outward on opposite sides of the vertical plane con taining said fulcrum.

3. The apparatus of claim 1 wherein said weight-supporting means is a rigid bar having an upper end pivoted to the inner sheave and a lower end pivoted to the counterweight.

4. The apparatus of claim 1 wherein said fulcrum includes a riser extending upwardly from a platform, and wherein said counterweight has a side facing and spaced from the riser and a bottom that is spaced above the platform when the inner boom is projected vertically upward from the fulcrum.

5. The apparatus of claim 1 including a support, and means mounting said inner boom on said support for pivotal movement of said inner boom through an angle of at least one hundred and eighty degrees about said fulcrum.

6. In a fluid transferreing apparatus, a tubular fluidconducting inner boom pivoted for elevational movement about a fulcrum, a tubular fluid-conducting outer boom pivoted in fluid-tight relation to the inner boom for elevational movement with respect thereto about an outer axis, an outer sheave secured to the outer boom in coaxial relation with the outer axis, an inner sheave, means mounting the inner sheave on the inner boom so that the axis of rotation of the inner sheave is on the opposite side of the fulcrum from said outer axis, a cable interconnecting the inner and outer sheaves for unitary rotation about their respective axes, a counterweight, and means mounting the counterweight on the inner sheave so that the counterweight is suspended from the inner sheave irrespective of the positions of the booms and so that the counterweight imposes a first turning moment about said fulcrum which counteracts the turning moment of the inner and outer booms about the fulcrum and a second turning moment about said inner sheaves axis which counteracts the turning moment of the outer boom about said outer axis, wherein said weight mounting means is an L shaped bar having an upper end pivoted to the inner sheave in radially spaced relation to its axis of rotation and a lower end pivoted to the counterweight.

References Cited UNITED STATES PATENTS 2,036,386 4/ 1936 Andersen 212-48 911,632 2/1909 Van Wie 212-48 2,927,607 3/1960 Bily 137-615 3,085,593 4/1963 Sorensen 137-615 Re. 25,855 9/1965 Mowell 137-615 ALAN COHAN, Primary Examiner.

H. M. COHN, Assistant Examiner. 

1. IN A FLUID TRANSFERRING APPARATUS, A TUBULAR FLUIDCONDUCTING INNER BOOM PIVOTED FOR ELEVATINAL MOVEMENT ABOUT A FULCRUM, A TUBULAR FLUID-CONDUCTING OUTER BOOM PIVOTED IN FLUID-TIGHT RELATION TO THE INNER BOOM FOR ELEVATIONAL MOVEMENT THROUGH SUBSTANTIALLY 360* WITH RESPECT THERETO ABOUT AN OUTER AXIS, AN OUTER SHEAVE SECURED TO THE OUTER BOOM IN COAXIAL RELATION WITH THE OUTER AXIS, AN INNER SHEAVE, MEANS MOUNTING THE INNER SHEAVE ON THE INNER BOOM SO THAT THE AXIS OF ROTATION OF THE INNER SHEAVE IS ON THE OPPOSITE SIDE OF THE FULCRUM FROM SAID OUTER AXIS, A CABLE INTERCONNECTING THE INNER AND OUTER SHEAVES FOR UNITARY ROTATION ABOUT THEIR RESPECTIVE AXES, A COUNTERWEIGHT, AND MEANS PIVOTALLY MOUNTING THE COUNTERWEIGHT ON THE INNER SHEAVE SO THAT THE COUNTERWEIGHT IS POSITIONED BELOW THE INNER SHEAVE IRRESPECTIVE OF THE POSITIONS OF THE BOOMS AND SO THAT THE COUNTERWEIGHT IMPOSES A FIRST TURNING MOMENT ABOUT SAID FULCRUM WHICH COUNTERACTS THE TURNING MOMENT OF THE INNER AND OUTER BOOMS ABOUT THE FULCRUM AND A SECOND TURNING MOMENT ABOUT SAID INNER SHEAVE''S AXIS WHICH COUNTERACTS THE TURNING MOMENT OF THE OUTER BOOM ABOUT SAID OUTER AXIS. 